Spring suspension for vehicles



April 13, 1954 A. F. HICKMAN 2,675,226

SPRING SUSPENSION FOR VEHICLES Original Filed May 8, 1947 4 Sheets-Sheet 1 fi INVENTOR.

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ATTORNEYS.

April 13, 1 A. F. HICKMAN SPRING SUSPENSION FOR VEHICLES 4 Sheets-Sheet 2 Original Filed May 8, 1947 INVENT 11,442.

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April 13, 1954 A. F. HICKMAN 2,675,226 SPRING SUSPENSION FOR VEHICLES Original Filed May 8, 1947 4 Sheets-Sheet 5 INVENTOR.

ATTORNEYS- April 13, 1954 2,675,226

A. F. HICKMA N SPRING SUSPENSION FOR VEHICLES Original Filed May 8, 1947 4 Sheets-Sheet 4 The main frame l of the vehicle can be of any suitable construction "and is shown as comprising a pair of longitudinal horizontal side frame bars in the form of inwardly facing channels iii, the central parts I! of whichare shown as converging toward the front of the vehicle and as depressed, as best shown in Fig. 2, relative to the front and rear ends 18 "and i9, re-* spectively, thereof. The central parts ll of these side frame bars of the frame are shown as connected by a pair of diagonal bars 2!]. Across bar 2| is shown as connecting'the extreme forward ends of the longitudinal side bars |6;'a

cross bar 22 is shown as connecting these longitudinal side bars at the rear ends of the parallel forward portions I8 thereof; a cross bar 23 is shown as connecting the extreme rearward ends of these longitudinal side frame bars; and a cross bar 24 is shown as connecting the forward ends of the rear parallel extremities l9 thereof.

lhe entire vehicle chassis, together'with its spring suspension, is constructed substantially symmetrically about a vertical longitudinal medial plane, and hence it is deemed sufficient to confine the following detailed description to the one (left) side of the vehicle, it being un- I derstood that this description and the same reference numerals apply to the opposite (right) side of the vehicle.

The front end of thevehicle' chassis or frame is supported on a front steering "axle 25*which is shown as being in the form of an I-beam extending'transversely of the frame l5 substantially centrally with reference to the front'cross bars 2| and 22 of the vehicle frame. A pair of extensions in the form of plates '26, is shown as welded to each end of the front steering axle to the front and rear edges of the'flanges thereof, these plates being of the same shape and extending outwardly from the ends of the axle in parallel spaced relation. These plates also extend upwardly from the ends of the axle and 4 tube 4|! is disposed parallel with the tube 30, that is, it diverges forwardly in a horizontal plane.

This crank arm is shown as comprising a pair of tubes 42 and 43 each having one end welded to the tube All and each bent so that their opposite ends 44, 45 are arranged in oppositely directed coaxial relation to each other. To provide additional strength a small bracing plate 46 is shown as welded to the tube 4|] intermediate the arms 42am 43 and as extending along and welded to the opposing surfaces of these arms, as best shown in Fig. 7.

The front and rear ends 4d and 45 of each crankarm 4| are. journaled on the main frame l5 of the vehicle to fulcrum about an axis extending parallel with the tubes 3|] and All, the fulcrum axis of these crank arms 4| thereby diverging toward the forward end of the vehicle. For this purpose the end 44 of the front tubular arm 42 of the crank arm 4| is shown as journaled in a bearing 48 secured to the extreme forward end of the corresponding longitudinal side frame bar N5 of the vehicle frame. This bearing 48, as best shown in Fig. '7, is preferably in the extreme upper ends of these plates are I formed to provide arms 28 which extend horizontally inward toward the vehicle frame I5 to provide a pair of axle brackets at each end of the axle 25. Each of the plates 25 is also formed to provide a horizontally outwardly projecting ear 29 for a purpose which will presently appear.

'A tube is welded to the inner extremities of the arms 28 of each pair of plates 26, as best shown in Figs. 6 and '7, these tubes 3|! extending longitudinally of the vehicle in a' horizontal plane but preferably being arranged in forwardly' diverging relation to each other as best shown in Figs. 1 and 3. Each of the tubes 30, as best shown in Fig. 7, has a pair of axle pivot pins 3| which are secured therein and project from opposite ends thereof. The projecting ends of these axle pivot pins are secured by shackles 32 of a shackle structure indicated at 33. with similar crank arm pivot pins 39 secured to and projecting from opposite ends of a tube forming the free end or outwardly offset portion of a crank arm' indicated generally at 4|. This the form of a bushing 49 of lubricant impregnated material encased in a metal sleeve 5|], this sleeve being in turn held in a bore of a bracket 5|. This bracket is shown as being T-shaped in horizontal section, having a side flange 52 which is secured against the outer face of the corresponding longitudinal side frame bar It and having-a transverse flange 53 which is secured against the forward face of the front cross bar 2| and projects laterally outwardly from this cross beam as best shown in Fig. 3-.

The rear end of each crank arm M is shown as journaled in a ball-and-socket bearing indicated generally at55. For this purpose, as best shown in- Fig. 7, a rearwardly opening socket member 56 is shown as welded to the rear end 45 of the crank arm and in this socket is fitted a spherical bearing member 58 of lubricant impregnated material encased in a spherical metal shell 59; An opening is provided through the rear end of I each spherical bearing member 58 and its shell 59- and the stem fill of a ball 6| fitted in the spherical bearing member 58 projects through this opening. This stem 60 can be secured to the frame of the vehicle as by bolting it to a bracket 62 which is in turn suitably secured to the cross bar 22 of the vehicle frame. It will be seen that with the bearings 48 and the crank arm 4| is free to turn about a fulcrum axis which extends lengthwise of the vehicle frame, the ball-and-socket bearing 55 permitting a degree of frame twist without strain upon the parts. It will also be seen that these fulcrum axes for the crank arms 4| at the front end of the vehicle diverge forwardly in a horizontal plane.

The forward end of each crank arm il extends through an :opening in the transverse flange 53 of the corresponding bracket 5| and connects with a rubber torsion spring secured to this flange and indicated generally at 65. This rubber torsionspring, as best shown in Fig. '7, is preferably constructed as follows:

The-numeral 66 represents a generally cylindricalrubber body having a coaxial bore through which the forward end 44 of the corresponding crank arm extends and having inwardly dished conical ends. In these inwardly dished ends of the rubber body are fitted front and rear conical plates Stand 69, these being vulcanized to the inwardly dished'end facesofthe rubber body.

to provide a flrm bondtherebetweona A disk endsr- In each ofatheswboresids arrangedr a cupw "l is e-suitably secured tc ---tl-1e rear conical lplate shaped bearingbushinaul 08JWhi0h zislspreferabl GB and this diskin turn is-secured to the transmade of lubricant impregnated nnaterial and :i verse-flange 53 of the brackem A disk H isencased in a cup shapedrmetal: shell lllS tthicliiiS suitably secured to the front=conica1 plate =68; inturn, presmfittedfilnthe lborellctct Each ofathem. thisdisk;-'in turmbeing fast to an annular-flange bearing bushings lfla fits the endofi the corre=-r- 12 of a hub ?3 on the forward endot thacranl; sponding pin sl on3 Biand it will ibeanotedthat armdl, this end l-t-'extending throu gh coaxial the endfaces of thesenpinsare engaged by the. apertures =provided-= in the conical plates 68; 69 it bearing bushingsei OB so that all thnnst forces re= and disks 16; H Thehub-13 ean' be secured to sulting from brake or dr-iife torquatreactions are the-forwardend 44 of the crank-armAl as by the taken by these bearings. it Thelshackles at each pin -'74 shoWn--'and-it wi11--be understood'that an 1 end of the axle'are connected :together. by a tie adjustable connection -(notshowno can beprored I Hi, this tie -rod having:am enlarged centralrz vided' between any of thepartss44, new 68 on part 4 i l and. reducedthreadedJendsml [Zilthesen between any oftheparts wfdfl on 53to;provide-=l5- threaded ends H2 extending: through; centralz. any desired initial-tensiom or wind-up of the r b openings. 1 I3 in. the shackles 132;" these shackles her-body 66. hearing againststhevannulaizshoulders j l4 lpross.

Asquare b1ock-16having aninverted cylindrical" vided. by u d e ds 23 Nutal l5 1101(1 socket 18 is a welded between each pair of the thecompanion shacklessl32 :against the shoulders-v, plates 25 which form spaced extensions 0f :the 20 1H5. It Will also particularly be noted that the. ends-oftheaxle 25, this blo'ck being welded nearsha'lkles 32 Slant-"upwardlyLand-1inwaldlyi-fmmt the upper ends-of =these platesl -A -squareblockthe crank, arm pivot:pins 9- dh axlefipivotl 79*is similarly Welded between each pair of the P 1 plates-26below theblocksJ6andinverticala1inee re r drive axle a is of conventionallc ment therewith; These-square block-s -16 and-Tel 25 tubular form tohouse the axleupowershaftsllH, are al osho a connected by a t l s connecting the difierential Jwithinra differential; ing plate H which alsotconn cts theupper edgeshousing I22 withther rearcdrive svheelsi'lfianeachi: of the plates 25 andcan be -Welded in place in of which is mountedtonaarspindlelinotishownl any suitable manner, This lower 1 k-19 i at each end of the axle:25a;: "Ihe.rearsaaxle as.-l.

provided with a verticatthreadeclbore 80in axial Sembiy 01098 1101? have y' fi alinementwiththe inverted socket 18 of the block pin m y but since in=- 0ther:- re p ct -thew iii,- A kingpinmeI-nber 31- is journaled in'bearrear axle assembly is similar: tox-thezfrontaaxle: 1 .32 and g3 provided in theljnverfied t assembly the same reierencenumerals rh'avejceen: i8 and threaded bore 80; respectively, andthisl l d d d st nguished;byztheisufiixpfajf king pin member is pmvidd-withuppepand 1 3;; Thus, a pair of plates 26a sareaweldedito thes.

pivct pin -g gg q in t front and rear sides of eachtend ofnthe rearwaxle, bearings 3 and g3 and a hcrizontany outwardly 25a to project upwardly therefrom andsupport at extending arm whichucarrjestthe conventional horizontal fcre-and-aft tuber-30a for. thelaxle-t king pivot pins of a shackle structureaindicated.at33a1fl The bearing bushing -89-forthe bearing 82 is 40 which carry the shackles 132a. These shacklesm preferably an inverted -cup-shapedbushing of 32a are connected togetherLby a tier r0;d=.l iliaxsimi-x lubricant impregnated material lm a cuplar to the tie rods Hi] .and;:carrylthelcrankarml:

shaped metal holder 9il fitted in the inverted p vo pins pr ject om =tha tubew lflacwhicha Socket 7g the-bearing bushing for the forms theoutlenend lof 'thestuhulan crank'tarmzr; bearing 5531s preferably a cup-shape bushing Ma. The forwardend of rthis crankiarmisflours fitted i a cup-shapedmetal:holder-fizlwhichjs, in naled in a hall-andsocket bearing atsecuredto;

turn fittedinra n externallythreaded-metal bushthe OI'OSS bar and:preferably:L'constrtictedh m ast d intg th lthr g ba 39 of the identical to the ball1andsocket=.bearing 55fiatthee lower block 9 Theumovement f the kingpin front end of the chassis, andtherean end is joura-n membe s; i yieldingly restrainedpin t 50 naled in a bearing Marci a1=bracket5ianarriedby ment aboutthe axis of the-bearings 82, 83 andfor he rear cross bar 23 and extends throughthis this purpose rubber blocks-94-are -sh0wn-as se- CTOSS bar to connect With/afirllbber p cured tenths opposingfacesofeach pair offlates Each rubber spring a has acylindrical jrubber ZB' -and in-contaet with the frontand rearsides body 5541 fast to a r plate 'iiuhavin Ethan-1 ofllthgarm 33. of th .king-pjnmember 3 nular flange 12a .fast to the rear. enclaof the crank? Each steering Wheel v1 is journaled on r r arm 45a and is preferably= identical with ethe ing spindle 85; this steering :spindle being- 1v; rubber springs 55a and .is mounted :on the-rear otally mounted on theupperanddowerends of" cross bar 23 of the vehiclerframe in the same" thgking pin ggvm t conventional mannerland manner and hence this description; is not rehaving'an intearal" steering -arm--96 *WhiChpro- 6O peated. It will he seenthatexceptsforthe steer jects rearvvardly therefrom of these teep. 111g gear and thezaxesrof Crank ing-arms til-is shown as connected by a horizontal armg and tubes and in transverselink 98 to the rearwardly projecting 3 diverging d thasuspension at thearm ggr of asteermg mechanism mg This Steer; rear end of the 1 vehicle 'iswsubsta-ntiallysimilar mechanism is shown as mounted centrally on t0 the suspension front end Ofthe Vehicle the real. side the steeringlaxlerzanand can be and hence a detailed description'isnot repeated. either mechanical or hydraulic; If a mechanical 111 the Operation of th suspensionpthe upward steering gear is used the Steeringmech'anigm mg movement of one end of ,thafront or :steer-ingaxle can be connected to the steering column through 25, fi 13116 Shackles w gs th e-outer'end a splined connection (not shown'); If; a hy- 0 of the crank arm ii pW dly,- heful r m f drauiic steering gear is used the steering mechathis crank arm oscillating-about-its bearings-48 nisrn can be connected to the steeringcolumn by and which are fast to the chassis frame IS:

a hose fitting-(not shown). This rotation of the crank armris yieldingw "re-3 Each shacl-z-le 32 :isin the term of a metal --link sisted by the corresponding rubber torsion-spring" having bores! tfi extending through its opposite 65, this movement of the crank'arm-being-transmitted to the forward end of the rubber body 66 through the pin 14, hub E3, flange 12, disk II and conical end plate 68, the latter being vulcanized to this rubber body, and the rear end of the rubber body being fast to the chassis frame through the vulcanized conical end plate 69, disk "to and flange 53 of the bracket 5| secured to the main frame. The front rubber torsion springs 65 thereby provide the yielding support for the front end of the chassis frame l5.

Similarly, the upward movement of the one end of the rear axle housing 25a, through the shackles 32a, swings the outer end of its crank arm Ma upwardly, this crank arm swinging about its bearings 48a and 55a on the chassis frame. This rotation of the crank arm Ma is yieldingly resisted by the rubber torsion springs 35a, the rubber body 66a of each of which is connected at its rear end to the crank arm Ala and at its front end to the chassis frame iii in the same manner as with the front rubber torsion springs at. These rubber torsion springs thereby provide the yielding support for the rear end of the chassis frame 15.

It will be noted that the shackles 32, 32a are inclined upwardly and inwardly from the crank arm pivot pins 39, 39a to the axle pivot pins 3 l, 3 la. This upward and inward inclined arrangement of these shackles tends to cause each axle to centralize itself in a direction transverse of the chassis and enables the action of gravity to geemetrically and resiliently resist any such move ment of the axle away from its central position. This permits the vehicle body to move substantially straight ahead despite a certain amount of lateral movement of the axle. I his arrangement or the shackles further provides high and wide pivot positions which provide increased stability in that it provides effective spring centers which can be as wide or wider than the track of the vehicle. Further, this arrangement of the shackles reduces sidesway, the high and wide pivot positioning, together with the upward and inward slant of the shackles, providing a suspension in which the vehicle body is more nearly suspended than mounted. Other important advantages which fiow from the inclined arrangement of the shackles are the reduction in the possibility of wheel tramp and in the elimination of the need for anti-body-roll devices, such as torsion bar stabilizers.

When one end of either axle 25, 25a is so forced upwardly relative to the chassis, the effective resilient opposing force of the rubber torsion springs 65, 65a increases at a geometric rate and not at an arithmetic rate. In this particular case the geometric rate is of the accelerated increase type in which increments of vertical movement of the axles are opposed by an accelerated rate of resilient resistance. This is primarily due to the progressive decrease in the efiective leverage of the crank arms M, Ma as they swing upwardly and inwardly about their axes of rotation. This action is also influenced by the varying angularity of the shackles 82, 32a and the fact that increments of vertical displacement of the pivot pins 39, 39a cause accelerated rates of increase in the angular displacement of the rubber torsion springs 65, 65a. This latter is due to the fact that increments of vertical movement of said pivot pins 39, 39a are not proportional to the accompanying increments of angular twist to which their companion rubber torsion springs 65, 65a are subjected.

This geometric action also occurs when either axle moves downwardly relative to the chassis. Throughout this particular movement the geometric action is of the accelerated decrease type, that is, as either axle passes'through increments of downward movement the rate of decrease of the resilient force tending to push the axle downwardly decreases.

Bythis means, so far as vertical forces are concerned, the vehicle chassis is free to float along solely under the influence of gravity (plus whateververtical momentum forces are present), this feature being or" particular significance when it is realized that the load carried by the vehicle is also; at this time, solely under the influence of gravity (plus whatever vertical momentum forces are present). The consequence is that,

within this particular range of movement, the

load in the vehicle moves vertically upand down with the same acceleration and deceleration as the body and hence without changing the pressure between the load and the body. Such a desirable result is quite difierent from that obtained from the conventional leaf spring suspension in which the axle and the rest of the unsprung weight drags or jerks down the body whenever the strains imposed on the chassis are negative. With the present suspension no such negative force, tending to pull the body downwardly is possible.

Another important advantage obtained by the angular arrangement of the shackles 32, 32a is that it eliminates wheel tramp. This latter may be broadly defined as a periodic vibration of either axle in a vertical transverse plane, the definition being usually limited to a rotary movement about an axis of rotation located at some point in the axle. In general it may be said that if one wheel is lifted and if this movement causes a downward thrust on the opposite wheel, then wheel tramp results. Such wheel tramp is prevented in the present suspension by ensuring that the downward thrust of any axle pivot 3i, Bic lies in a plane directed toward the contact of the tire with the road. When such a condition ob tains, a vertical upward thrust against one wheel is opposed by 2. directly opposite force passing through the corresponding axle pivot 3 I, am and hence no downward thrust is imposed upon the opposite wheel as occurs in the conventional leaf spring suspension.

The axles, particularly the front steering axle, are additionally subject to periodic vibrations in a horizontal plane, such vibration being encouraged every time one wheel or the other encounters even a small undulation in the road. Thus, every time the wheel goes over a rising undulation or through a depression in the road, the wheel must speed up and slow down in its rotation because the line of contact between the tire and the road becomes longer than a straight line. This constant change in wheel rotational speed is, of course, transmitted to the axle and if this change in wheel speed is compelled to be instantaneous the vibrations set up in the axle assembly grow to the condition commonly known as wheel shimmy which, in an aggravated condition, renders steering the vehicle impossible. Further, when this change in wheel rotational speed is compelled to be instantaneous the wheel will tend to hop, this not only resulting in further undesirable vibrations escaping to the axle and steering gear, but also causing uneven wear around the periphery of the tire, this being commonly known as tire cupping. The escaping vibrations due to instantaneous change in wheel rotational 1 speed in traveling over an undulating road are further aggravated by the gyroscopic forces inherent in the rotating wheels and lead topronounced body shake, violent periodic vibration of the axle assembly and uncontrollable steering.

Such instantaneous change in wheel rotational speed can be avoided" by permitting thewheels to move in a generallyhorizontal plane longitudinally of the vehicle, it being also necessary-to restrainthis free'dompf the wheels if the undesirable efiects of instantaneous change in wheel speed is to be avoided." With such -restrained movement of the wheels longitudinally of the vehicle, the wheels are permitted to yieldingly move lengthwise oi the vehicle in response to the changes in speed of the wheel thereby to provide time for the changes in rotational speed of the wheels.

With the present suspension the king pin member or arm BI is capable of moving about the axis of the pins 8d, 85, this movement being restrained and the king pin 88 centered by the opposing rubber pads 94. It will be seen that movement of each steering wheel 15 longitudinally of the chassis is permitted under the resilient restraint of the rubber pads, this providing the necessary time to allow for changes in wheel rotationa1 speed in passing over an undulating road so as to avoid the generation of undue vibrations in the axle and steering gear and uneven wear of the tires. With the steering gear arranged as shown it will be seen that such movement of either steering wheel :5 around the axis of the pins 8 85 will not change the longitudinal direction of the steering wheel and that the steering is wholly under control of the steering gear. The present invention thereby allows each of the front steering wheels to move longitudinally of the vehicle frame against a resilient resistance of any desired spring rate and without allowing the wheels to change the direction of their travel in relation to the steering gear regardless of the position of the steering gear.

The present invention provides resilient support for the vehicle frame in the form of simple and sturdy rubber torsion springs which can be produced at low cost and are secured both to the frame of the vehicle and also to the crank arms of the suspension in a simple and effective manner and in position where they are readily accessible. Further, the suspension as a whole can be readily designed to have any characteristics within an operative range. Thus, any desired resistance curve can be obtained by making the crank arms 4|, lla of a corresponding length and any desired frequency can be obtained by selecting a rubber spring 65, 55a of such diameter as to provide the angular crank arm movement to provide such desired frequency. The use of the rubber springs 65, 65a of the form shown and in relation to the crank arms 4!, Ma, shackles 32, 32a and axle pivots as shown provides this ability to provide any desirable spring rate and resistaance curve in a very simple and inexpensive vehicle suspension.

From the foregoing it will be seen that the present invention provides a very simple and sturdy spring suspension in which any desired operating characteristics can easily be obtained.

I claim:

1. A vehicle spring suspension for connecting the frame structure and axle structure of a vehicle and comprising a pair of spaced coaxial bearings mounted on one of said. structures and haying-,theiraxis arranged IeBgthWise-ofnsaid frame-structure, a crankarmhaving longitudinally spaced ends and an onset-part normally proj ectingin a horizontal direction with said ends journaled in said bearings and with one of said ends projecting beyond. the. corresponding bearing, shackle means pivotally connecting said offset part of said crank arm with the other of said structures, and resilient meansto resist rotation of said crank arm comprising a rubber body having aboreextending therethrough and through which said cne of said ends-of-said crank extendsymeansconnecting said one of said ends of said crank arm with the side of said rubber body remote from said oflset part, and means anchoring the other side of said rubber body on said one of said structures on the side of said corresponding bearing remote from said offset part of said crank arm.

2. A vehicle spring suspension for connecting the frame structure and axle structure of a vehicle and comprising a spherical socket bearing member, a companion bearing member of a ball form fitted in said socket bearing member, one of said bearing members being secured to one of said structures, a sleeve bearing secured to said one of said structures in spaced relation, lengthwise of said frame, to one of said bearing members, a crank arm having longitudinally spaced ends and an oiTset part normally projecting in a horizontal direction, the other of said bearing members being fast to one of said ends of said crank arm and the other end of said crank arm being journaled in and projecting beyond said sleeve bearing, shackle means pivotally connecting said offset part of said crank arm with the other of said structures, and resilient means to resist rotation of said crank arm comprising a rubber body having a bore extending therethrough and through which said projecting end of said crank arm extends, means connecting said projecting end of said crank arm with the side of said rubber body remote from said offset part, and means anchoring the other side of said rubber body on said one of said structures on the side of said sleeve bearing remote from said offset part of said crank arm.

3. A vehicle spring suspension for connecting the frame structure and axle structure of a vehicle and comprising a pair of spaced coaxial bearings mounted on one of said structures and having their axis arranged lengthwise of said frame structure, a crank arm having longitudinally spaced ends and an oiiset part normally projecting in a horizontal direction with said ends journalled in said bearings and with one of said ends projecting beyond the corresponding bearing, shackle means pivotally connecting said ofiset part of said crank arm with the other of said structures, and resilient means to resist rotation of said crank arm comprising a rubber body, means connecting said one of said ends of said crank arm with one side of said rubber body, and means anchoring the other side of said rubber body on said one of said structures.

4. A Vehicle spring suspension for connecting the frame structure and axle structure of a vehicle and comprising a spherical socket hearing member, a companion bearing member of ball form fitted in said socket bearing member, one of said bearing members being secured to one of said structures, a sleeve bearingsecured to one of said structures in spaced relation, lengthwise of said frame, to said one of said bearing members, a crank arm having longitudi- 12 anchoringthe other side of said rubber body on one of said structures.

References Cited in the file of this patent UNITED STATES PATENTS Number Name Date 1,919,033 Noble July 18, 1933 2,137,848 Macbeth Nov. 22, 1938 2,153,083 Griswold Apr. 4, 1939 2,173,973 I Leighton Sept. 26, 1939 2,203,344 Tjaarda June 4, 1940 2,450,506

F'logaus Oct. 5, 1948 

